Transmission for hybrid electric vehicle

ABSTRACT

A transmission for a hybrid electric vehicle may include an input element, an output element, a first motor generator, a second motor generator, a first planetary gear set where the input element, the output element, and the first motor generator may be connected, a second planetary gear set where the output element and the second motor generator may be connected, a third planetary gear set, and a first clutch and a second clutch.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application claims priority to Korean Patent Application Number 10-2010-0058118 filed Jun. 18, 2010, the entire contents of which application is incorporated herein for all purposes by this reference.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a transmission for a hybrid electric vehicle, and more particularly, to an electrically variable transmission (EVT) that implements a continuous transmission gear ratio, using one or more planetary gear sets and motors.

2. Description of Related Art

The EVTs in the related art can be classified into a single mode type and a multimode type. The single mode type, as shown in FIG. 1, typically uses a planetary gear set 500 that has a configuration in which input from an engine is supplied to a carrier C and output is achieved through a ring gear R, and a first motor generator MG1 is connected to a sun gear S and a second motor generator MG2 is connected to ring gear R.

The relationship of torque in the EVT can be briefly shown, as shown in FIG. 2, that is, torque from first motor generator MG1 and the output shaft is applied from both sides, with respect to torque supplied from the engine to carrier C, such that they keep balance.

Therefore, first motor generator MG1 should keep supplying appropriate reaction force to transmit the torque of the engine well to the output shaft, such that the torque of the output shaft is necessarily smaller than the torque of the engine. Further, the amount of power transmitted from the engine along an electric path which is made through first motor generator MG1 and second motor generator MG2 considerably increase in an acceleration section of the vehicle, such that efficiency decreases and motor generators having large capacity are required.

Although the multimode types of EVTs have been proposed to overcome the defects described above, most of the EVTs are provided with an ENGINE ONLY mode for starting a vehicle due to various limits for the characteristics of batteries and motor generators.

That is, in wide open throttle (WOT) start in which a driver rapidly starts a hybrid electric vehicle by maximally pressing down the acceleration pedal, it is difficult to ensure sufficient output shaft torque due to limits in the batteries and motor generators in the multimode types of EVTs of the related art, such that the specific ENGINE ONLY mode is provided for the rapid acceleration start only by the engine, such that the user's request is satisfied.

Further, as described above, in order to overcome the practical limits in the batteries and motor generators, various modes including the ENGINE ONLY start mode are provided and the number of clutches used to switch the modes is increased; however, as a plurality of clutches is provided, transmission efficiency of the EVT decreases, and new problems, such as complicity in the control of switching the modes and shock in switching the modes, occur.

Further, the shock due to switching the modes is generated and acceleration response of the vehicle decreases when the modes are frequently switched in the WOT start. In particular, it is impossible to continuously increase the number of revolution of the engine in the WOT start in the multimode type of EVT of the related art and it is required to reduce the number of revolution of the engine at a predetermined level in order to switch the modes, such that control is difficult, transmission shock is easily generated, and the acceleration response decreases.

For example, the EVT shown in FIG. 3 is a 2-mode EVT having a fixed gear ratio and can be illustrated by the lever diagram of FIG. 4. In the EVT, a vehicle is started at the first stage with a fixed gear ratio which is implemented by engaging only a firsts clutch CL1 with a fourth clutch CL4 in the WOT start and a first planetary gear set PG1 and a second planetary gear set PG2 become integral by the engagement of fourth clutch CL4 and rotate with the same number of revolution as the engine connected to an input shaft. Further, a third ring gear R3 of a third planetary gear set PG3 is fixed by first clutch CL1, such that the power of the engine that is inputted to a third sun gear S3 of third planetary gear set PG3 is reduced and transmitted the an output shaft through a third carrier C3.

As the vehicle speed increases, the engine is supposed to operate close to the maximum power point such that the maximum acceleration force is acquired, but as the vehicle speed increases, the operation point of the engine exceeds the maximum number of revolution.

In this state, the power of the engine is supposed to directly supplied from second carrier C2 to third carrier C3 by engaging a second clutch CL2, but in this state, there is necessarily a large difference between the rotation speeds of second carrier C2 and third carrier C3, such that it is required to synchronize the rotation speeds of second carrier C2 and third carrier C3 by reducing the speed of the engine. As a result, it becomes worse to control the EVT and transmission shock is likely to be generated, and the acceleration response decreases with the decrease in rotation speed of the engine.

The information disclosed in this Background of the Invention section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.

BRIEF SUMMARY

Various aspects of the present invention are directed to providing a transmission for a hybrid electric vehicle that can more effectively transmit the torque from an engine to an output shaft, provide sufficient power performance in WOT start, achieve excellent controllability without generating transmission shock by allowing modes to be naturally and smoothly switched, and ensure excellent acceleration response.

In an aspect, the present invention provides a transmission for a hybrid electric vehicle, including an input element where rotation power may be inputted and an output element from which the rotation power may be outputted, a first motor generator and a second motor generator, a first planetary gear set where the input element, the output element, and the first motor generator may be connected, a second planetary gear set where the output element and the second motor generator may be connected, a third planetary gear set, and a first clutch and a second clutch, in which a first rotary element of the first planetary gear set and a first rotary element of the second planetary gear set may be kept connected with the output element, a second rotary element and a third rotary element of the first planetary gear set may be connected with the input element and the first motor generator, respectively, a second rotary element of the second planetary gear set may be connected with the second motor generator, a first rotary element of the third planetary gear set may be kept connected with one rotary element other than the first rotary element of the first planetary gear set and the second rotary element of the third planetary gear set may be kept connected with one rotary element other than the first rotary element of the second planetary gear set, the first clutch may be disposed to switch a rotatable state of a third rotary element of the second planetary gear set, the second clutch may be disposed to selectively connect a third rotary element of the third planetary gear set to at least one or more rotary elements in the rotary elements that may be not kept connected with the third planetary gear set in the rotary elements of the first planetary gear set and the second planetary gear set.

In another aspect, the present invention provides a transmission for a hybrid electric vehicle, including a first planetary gear set having three rotary elements connected with an input element, an output element, and a first motor generator, respectively, a second planetary gear set including three rotary elements having the rotary element connected to the output element and the rotary element connected to the second motor generator, third planetary gear set PG3 including a first rotary element kept connected with the rotary element connected with input element INPUT of first planetary gear set PG1, a second rotary element kept connected to the rotary element connected to second motor generator MG2 in second planetary gear set PG2, and a third rotary element that may have the same rotation speed as at least one rotary element in the other rotary elements of first planetary gear set PG1 and second planetary gear set PG2 other than the rotary elements kept connected to the first rotary element and the second rotary element kept, second clutch CL2 selectively connecting the third rotary element of third planetary gear set PG3 to the rotary elements having the same rotation speed in the other rotary elements of first planetary gear set PG1 and second planetary gear set PG2 other than the rotary elements kept connected to the first rotary member and the second rotary member of third planetary gear set PG3, and a first clutch switching a rotatable state of the other one rotary element that may be not connected to the output element and the second motor generator, in the rotary elements of the second planetary gear set.

According to various aspects of the present invention, it may be possible to more effectively transmit the torque from an engine to an output shaft, provide sufficient power performance in WOT start, achieve excellent controllability without generating transmission shock by allowing modes to be naturally and smoothly switched, and improve acceleration response.

The methods and apparatuses of the present invention have other features and advantages which will be apparent from or are set forth in more detail in the accompanying drawings, which are incorporated herein, and the following Detailed Description, which together serve to explain certain principles of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a diagram illustrating the configuration of a single mode type of EVT according to the related art.

FIG. 2 is a lever diagram illustrating a torque relationship of the EVT shown in FIG. 1.

FIG. 3 is a diagram illustrating the configuration of a 2-mode EVT according to the related art.

FIG. 4 is a lever diagram illustrating the EVT shown in FIG. 3.

FIG. 5 is a diagram illustrating the configuration of a transmission for a hybrid electric vehicle according to various exemplary embodiments of the present invention.

FIG. 6 is a diagram illustrating the configuration of a transmission for a hybrid electric vehicle according to various exemplary embodiments of the present invention.

FIG. 7 is a lever diagram illustrating the exemplary embodiments shown in FIG. 5.

FIG. 8 is a lever diagram briefly illustrating a torque relationship of the EVT shown in FIG. 7.

FIG. 9 is an operation mode table of the exemplary embodiment shown in FIG. 5.

It should be understood that the appended drawings are not necessarily to scale, presenting a somewhat simplified representation of various features illustrative of the basic principles of the invention. The specific design features of the present invention as disclosed herein, including, for example, specific dimensions, orientations, locations, and shapes will be determined in part by the particular intended application and use environment.

In the figures, reference numbers refer to the same or equivalent parts of the present invention throughout the several figures of the drawing.

DETAILED DESCRIPTION

Reference will now be made in detail to various embodiments of the present invention(s), examples of which are illustrated in the accompanying drawings and described below. While the invention(s) will be described in conjunction with exemplary embodiments, it will be understood that present description is not intended to limit the invention(s) to those exemplary embodiments. On the contrary, the invention(s) is/are intended to cover not only the exemplary embodiments, but also various alternatives, modifications, equivalents and other embodiments, which may be included within the spirit and scope of the invention as defined by the appended claims.

Referring to FIG. 5, a first exemplary embodiment of the present invention includes: an input element INPUT where rotation power is inputted and an output element OUTPUT from which the rotation power is outputted, a first motor generator MG1 and a second motor generator MG2, a first planetary gear set PG1 where input element INPUT, output element OUTPUT, and first motor generator MG1 are connected, a second planetary gear set PG2 where output element OUTPUT and second motor generator MG2 are connected, a third planetary gear set PG3, and a first clutch CL1 and a second clutch CL2.

In this configuration, the first rotary element of first planetary gear set PG1 and the first rotary element of second planetary gear set PG2 are kept connected with output element OUPUT, the second rotary element and the third rotary element of first planetary gear set PG1 are connected with input element INPUT and first motor generator MG1, respectively, the second rotary element of second planetary gear set PG2 is connected with second motor generator MG2, the first rotary element of third planetary gear set PG3 is kept connected with a rotary element except for the first rotary element of first planetary gear set PG1, and the second rotary element of third planetary gear set PG3 is kept connected with a rotary element except for the first rotary element of second planetary gear set PG2.

Further, first clutch CL1 is disposed to be able to switch a rotatable state of the third rotary element of second planetary gear set PG2, second clutch CL2 is disposed to selectively connect the third rotary element of third planetary gear set PG3 with at least one or more rotary elements of the rotary elements that are not kept connected with third planetary gear set PG3, in the rotary elements of first planetary gear set PG1 and second planetary gear set PG2.

In the exemplary embodiment, second clutch CL2 is disposed to be able to simultaneously connect or disconnect the first rotary element of first planetary gear set PG1 and the first rotary element of second planetary gear set PG2, which are both connected to the output element, with or from the third rotary element of third planetary gear set PG3.

Further, in order to make a fixed gear stage when second clutch CL2 operates, a third clutch CL3 is further included to switch a rotatable state of one rotary element, which is not connected with output element OUTPUT and first clutch CL1, in the rotary elements of second planetary gear set PG2.

In the exemplary embodiment, one rotary element that is not connected with output element OUTPUT and first clutch CL1, in the rotary elements of second planetary gear set PG2, is the second rotary element of second planetary gear set PG2 where second motor generator MG2 is connected, such that third clutch CL3 is connected to the second rotary element.

A fourth clutch CL4 that selectively connects at least two rotary elements in the rotary elements of third planetary gear set PG3 may be further included. In the exemplary embodiment, fourth clutch CL4 selectively connects the rotary elements, which are kept connected with first planetary gear set PG1 and third planetary gear set PG3, with the rotary elements that are kept connected with second planetary gear set PG2 and third planetary gear set PG3, and is indicated by a dotted line in FIG. 5.

In the exemplary embodiment, first planetary gear set PG1 is a single pinion planetary gear set, in which the first rotary element is a carrier C1, the second rotary element is a ring gear R1, and the third rotary element is a sun gear S1. Obviously, the first rotary element of first planetary gear set PG1 may be a ring gear, the second rotary element may be a carrier, and the third rotary element may be a sun gear.

Second planetary gear set PG2 is a single pinion planetary gear set, in which the first rotary element is a carrier C2, the second rotary element is a sun gear S2, and the third rotary element is a ring gear R2.

Third planetary gear set PG3 is a single pinion planetary gear set, in which the first rotary element is a carrier C3, the second rotary element is a sun gear S3, and the third rotary element is a ring gear R3. Obviously, unlikely to the configuration described above, the first rotary element may be a ring gear, the second rotary element may be a sun gear, and the third rotary element may be a carrier.

The configuration of the first exemplary embodiment of the present invention described above may be concluded by the lever diagram shown in FIG. 7.

The arrangement state of torque applied to the lever showing first planetary gear set PG1 may be illustrated again, as shown in FIG. 8.

That is, for the torque exerted in output element OUTPUT, it may be considered that torque from an engine and torque from first motor generator MG1 are exerted at both sides, such that the torque is balanced.

Comparing the state of FIG. 8 with the state of the related art shown in FIG. 2, it can be seen that it is possible to transmit torque larger than the engine torque to output element OUTPUT, and when the path through which the power of the engine reaches output element OUTPUT is divided into a mechanical power path and an electrical power path, it can be seen that it is possible to relatively increase the relative importance of power transmission through the mechanical power path, such that it is possible to transmit high effective mechanical power, thereby achieving more larger acceleration force than the related art in the WOT start and reducing the size of the first motor generator MG1 because the importance of the electrical power can be reduced.

Since, as described, it is possible to achieve larger acceleration force in the EVT of the present invention than the fixed gear ratio mode that is the ENGINE ONLY mode applied to the 2-mode EVT of the related art, it is not required to switch to the ENGINE ONLY mode when starting, such that it is possible to make the configuration of the EVT more simple and decrease the clutches with the decrease of modes, and thus, it is possible to simplify the configuration and improve power transmission efficiency.

The operation in the WOT start of the EVT of the present invention is described with reference to the lever diagram of the EVT of the present invention shown in FIG. 7 and the operation mode table shown in FIG. 9.

The EVT of the present invention uses not the fixed gear ratio mode that is the ENGINE ONLY MODE, but an EVT-1 and EVT-2 modes, in the WOT start.

That is, driving is implemented in the EVT-1 mode in the early stage of the WOT start, in which only first clutch CL1 is engaged, the engine power is supplied to the second element of first planetary gear set PG1 through input element INPUT, an input division mode is implemented by operating second motor generator MG2 by using electricity generated by first motor generator MG1, and power is outputted to output element OUTPUT through the first element of first planetary gear set PG1 and the first element of second planetary gear set PG2.

In this state, since first clutch CL1 is engaged, as the vehicle speed increases, the rotation speed of second motor generator MG2 considerably increases in comparison to the rotation speed of the rotation force supplied to output element OUTPUT in accordance with the gear ratio of second planetary gear set PG2 and the number or revolution of second motor generator MG2 becomes too high when the engine operates close to the maximum power point, such that loss due to high-speed rotation starts to rapidly increase.

In the EVT of the present invention, it is switched to the EVT-2 mode that is a multiple split mode before the loss due to high-speed rotation of second motor generator MG2 rapidly increases, which is implemented simply by engaging second clutch CL2 and disengaging first clutch CL1.

That is, in the EVT of the present invention, it is possible to engage second clutch CL2 without a specific synchronizing process, when the number of revolution of the third rotary element of third planetary gear set PG3 becomes the same as the numbers of revolution of the first element of first planetary gear set PG1 and the first element of second planetary gear set PG2, such that it is possible to very simply control switching the modes and smoothly switch the modes without transmission shock, and accordingly, the acceleration response is improved.

Further, the torque directions of first motor generator MG1 and second motor generator MG2 are kept before and after the mode is switched, as described above, such that the control becomes easier.

The engine keeps operating at the maximum power point by the EVT-2 mode implemented as described above and the rotation speed of second motor generator MG2 gradually decreases with the increase in vehicle speed, such that it operates only within the limited operation range (for example, 12000 RPM) of the motor.

Further, in the EVT of the present invention, two fixed gear ratio modes can be additionally implemented without fourth clutch CL4 and two additional fixed gear ratio modes can be further implemented when fourth clutch CL4 is added, such that total four fixed gear ratio modes can be achieved.

That is, when first planetary gear set PG1, second planetary gear set PG2, and third planetary gear set PG3 are implemented in a multiple planetary gear that can be shown by one lever by engaging second clutch CL2 and the second rotary element of second planetary gear set PG2 is fixed by engaging third clutch CL3, a first fixed gear ratio mode FG1 in which the rotation speed of the output element increases with respect to the rotation speed of the engine is implemented.

Further, when first clutch CL1 is engaged instead of third clutch CL3, with second clutch CL2 engaged, the third rotary element of second planetary gear set PG2 is fixed, such that a second fixed gear ratio mode FG2 in which the rotation speed of the output element decreases with respect to the rotation speed of the engine is implemented.

Further, when fourth clutch CL4 is engaged, with only first clutch CL1 engaged, a third fixed gear ratio mode FG3 in which output further decreased than second fixed gear ratio mode FG2 is outputted to output element OUTPUT is implemented, and in a fourth fixed gear ratio mode FG4 in which only second clutch CL2 and fourth clutch CL4 are engaged, all of the rotary elements of first planetary gear set PG1, second planetary gear set PG2, and third planetary gear set PG3 are integrated by second clutch CL2 and fourth clutch CL4, such that the engine power is outputted at a transmission ratio of 1:1 to output element OUTPUT.

The several fixed gear ratio modes can significantly contribute to improving fuel efficiency of a vehicle by allowing the vehicle to travel without electric load. In particular, in first fixed gear ratio mode FG1 that is implemented by engaging second clutch CL2 and third clutch CL3, it is possible to considerably contribute to improving the fuel efficiency when the vehicle travels at high speed by providing an overdrive transmission ratio.

The second exemplary embodiment shown in FIG. 6 has a different configuration from the first exemplary embodiment, in which the first rotary element is a carrier C1, the second rotary element is a ring gear R1, and the third rotary element is a sun gear S1 in a first planetary gear set PG1, the first rotary element is a carrier C2, the second rotary element is a sun gear S2, and the third rotary element is a ring gear R2 in a second planetary gear set PG2, and the first rotary element is a carrier C3, the second rotary element is a ring gear R3, and the third rotary element is a sun gear S3 in a third planetary gear set PG3, and all of the planetary gear sets are single pinion planetary gear sets.

Further, second clutch CL2 is disposed between sun gear S3 that is the third rotary element of third planetary gear set PG3 and sun gear S1 that is the third rotary element of first planetary gear set PG2 and the detailed operation is substantially similar to that in the first exemplary embodiment.

Meanwhile, the exemplary embodiments of the present invention may be described as follows. The exemplary embodiments include first planetary gear set PG1 including three rotary elements connected with input element INPUT, output element OUTPUT, and first motor generator MG1, respectively, second planetary gear set PG2 including three rotary elements having the rotary element connected to output element OUTPUT and the rotary element connected to second motor generator MG2, third planetary gear set PG3 including a first rotary element kept connected with the rotary element connected with input element INPUT of first planetary gear set PG1, a second rotary element kept connected to the rotary element connected to second motor generator MG2 in second planetary gear set PG2, and a third rotary element that has the same rotation speed as at least one rotary element in the other rotary elements of first planetary gear set PG1 and second planetary gear set PG2 other than the rotary elements kept connected to the first rotary element and the second rotary element kept, second clutch CL2 selectively connecting the third rotary element of third planetary gear set PG3 to the rotary elements having the same rotation speed in the other rotary elements of first planetary gear set PG1 and second planetary gear set PG2 other than the rotary elements kept connected to the first rotary member and the second rotary member of third planetary gear set PG3, and first clutch CL1 that can switch the rotatable state of one rotary element that is not connected to output element OUTPUT and second motor generator MG2, in the rotary elements of second planetary gear set PG2.

Second clutch CL2 is disposed to connect/disconnect the third rotary element of third planetary gear set PG3 with/from the rotary element of first planetary gear set PG1 and the rotary element of second planetary gear set PG2, which are both connected to output element OUTPUT, in the first exemplary embodiment.

Second clutch CL2 is disposed to connect/disconnect the third rotary element of third planetary gear set PG3 with/from the rotary element connected to first motor generator MG1 in first planetary gear set PG1, in the second exemplary embodiment.

A third clutch CL3 may be further provided to switch the rotatable state of the rotary element of second planetary gear set PG2 which is connected with second motor generator MG2 such that a fixed gear ratio mode can be implemented while a fourth clutch CL4 may be further provided to switch the connection between at least two or more rotary elements of third planetary gear set PG3 such that an additional fixed gear ratio mode can be implemented.

The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. They are not intended to be exhaustive or to limit the invention to the precise forms disclosed, and obviously many modifications and variations are possible in light of the above teachings. The exemplary embodiments were chosen and described in order to explain certain principles of the invention and their practical application, to thereby enable others skilled in the art to make and utilize various exemplary embodiments of the present invention, as well as various alternatives and modifications thereof. It is intended that the scope of the invention be defined by the Claims appended hereto and their equivalents. 

What is claimed is:
 1. A transmission for a hybrid electric vehicle, comprising: an input element where rotation power is inputted and an output element from which the rotation power is outputted; a first motor generator and a second motor generator; a first planetary gear set where the input element, the output element, and the first motor generator are connected; a second planetary gear set where the output element and the second motor generator are connected; a third planetary gear set; and a first clutch and a second clutch, wherein a first rotary element of the first planetary gear set and a first rotary element of the second planetary gear set are kept connected with the output element, a second rotary element and a third rotary element of the first planetary gear set are connected with the input element and the first motor generator, respectively, a second rotary element of the second planetary gear set is connected with the second motor generator, a first rotary element of the third planetary gear set is kept connected with one rotary element other than the first rotary element of the first planetary gear set and a second rotary element of the third planetary gear set is kept connected with one rotary element other than the first rotary element of the second planetary gear set, the first clutch is disposed to switch a rotatable state of a third rotary element of the second planetary gear set, the second clutch is disposed to selectively connect a third rotary element of the third planetary gear set to at least one or more rotary elements in the rotary elements that are not kept connected with the third planetary gear set in the rotary elements of the first planetary gear set and the second planetary gear set.
 2. The transmission for the hybrid electric vehicle according to claim 1, further comprising a third clutch that switches a rotatable state of a rotary element, which is not connected with the output element and the first clutch, in the rotary elements of the second planetary gear set, in order to make a fixed gear stage when the second clutch operates.
 3. The transmission for the hybrid electric vehicle according to claim 1, further comprising a third clutch that switches a rotatable state of a rotary element, where the second motor generator is connected, in the rotary elements of the second planetary gear set, in order to make a fixed gear stage when the second clutch operates.
 4. The transmission for the hybrid electric vehicle according to claim 1, further comprising a fourth clutch disposed to selectively connect the rotary elements, which are kept connected with each other in the first planetary gear set and the third planetary gear set, with the rotary elements that are kept connected with the second planetary gear set and the third planetary gear set.
 5. The transmission for the hybrid electric vehicle according to claim 1, further comprising a fourth clutch disposed to selectively connect at least two rotary elements in the rotary elements of the third planetary gear set.
 6. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element of the first planetary gear set is a carrier.
 7. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element is a carrier, the second rotary element is a ring gear, and the third rotary element is a sun gear, in the first planetary gear set.
 8. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element of the first planetary gear set is a ring gear.
 9. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element is a ring gear, the second rotary element is a carrier, and the third rotary element is a sun gear, in the first planetary gear set.
 10. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element of the second planetary gear set is a carrier.
 11. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element is a carrier, the second rotary element is a sun gear, and the third rotary element is a ring gear, in the second planetary gear set.
 12. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element of the third planetary gear set is a carrier.
 13. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element is a carrier, the second rotary element is a sun gear, and the third rotary element is a ring gear, in the third planetary gear set.
 14. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element of the third planetary gear set is a ring gear.
 15. The transmission for the hybrid electric vehicle according to claim 1, wherein the first rotary element is a ring gear, the second rotary element is a sun gear, and the third rotary element is a carrier, in the third planetary gear set.
 16. A transmission for a hybrid electric vehicle, comprising: a first planetary gear set PG1 including three rotary elements, including a rotary element kept connected with an input element, a rotary element kept connected with an output element, and a rotary element kept connected with a first motor generator, respectively; a second planetary gear set PG2 including three rotary elements, including a rotary element connected to the output element and a rotary element connected to a second motor generator; a third planetary gear set PG3 including a first rotary element kept connected with a rotary element connected with the input element of the first planetary gear set PG1, a second rotary element kept connected to a rotary element connected to the second motor generator MG2 in the second planetary gear set PG2, and a third rotary element that has the same rotation speed as at least one rotary element in the other rotary elements of the first planetary gear set PG1 and the second planetary gear set PG2 other than the rotary elements kept connected to the first rotary element and the second rotary element kept; a second clutch CL2 selectively connecting the third rotary element of the third planetary gear set PG3 to the rotary elements having the same rotation speed in the other rotary elements of the first planetary gear set PG1 and the second planetary gear set PG2 other than the rotary elements kept connected to the first rotary member and the second rotary member of the third planetary gear set PG3; and a first clutch switching a rotatable state of the other one rotary element that is not connected to the output element and the second motor generator, in the rotary elements of the second planetary gear set.
 17. The transmission for the hybrid electric vehicle according to claim 16, wherein the second clutch is disposed to connect/disconnect the third rotary element of the third planetary gear set with/from the rotary element of the first planetary gear set and the rotary element of the second planetary gear set which are both connected to the output element.
 18. The transmission for the hybrid electric vehicle according to claim 16, wherein the second clutch is disposed to connect/disconnect the third rotary element of the third planetary gear set with/from the rotary element connected to the first motor generator in the first planetary gear set.
 19. The transmission for the hybrid electric vehicle according to claim 16, further comprising a third clutch that switches a rotatable state of the rotary element of the second planetary gear set which is connected with the second motor generator.
 20. The transmission for the hybrid electric vehicle according to claim 19, further comprising a fourth clutch that switches the connection between at least two or more rotary elements of the third planetary gear set. 